JPS6334344A - Intermittent drive device - Google Patents

Abstract

PURPOSE:To realize a smooth operation and stoppage without costing much labor on maintenance and custody by constituting a device with both drive and driven gears of a non-circle and a speed reducer or the like comprising an external tooth gear band meshing with an internal tooth gear. CONSTITUTION:A device is constituted with both drive and driven gears of a non-circle 2, 4 and a speed reducer or the like 5 comprising an external tooth gear band meshing with an internal tooth gear. And a reciprocation is made with a crank lever 25 swung with an eccentric cam which fixes the internal tooth gear of the speed reducer 5 to an input shaft 1, so only 1/2 revolution of a sine curved low speed revolution which is in motion and is transmitted to a middle shaft 3 is transmitted to an output shaft 6, and the remaining 1/2 revolution can stop the output shaft 6. In addition, its operation stoppage is generated during the continuous revolutions of the gear, so a change is made in a smooth curve, and no impact occurs, and the control of operation and stoppage is made with high precision, while no wear or the like occurs and the labor of maintenance and custody can be saved.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a device for intermittently feeding a tape-like object, a tape-like object such as cloth or paper, etc. by means of a feed roll and a pressure roll, and other devices that are operated intermittently. This invention relates to an improvement of an intermittent drive device.

2. Description of the Related Art A conventional intermittent drive device, as shown in FIG. , the ratchet wheel 105 is rotated intermittently to give intermittent rotation to the shaft 106, and the brake plates 110, 111 to which the brake shoes 108, 109 surrounding the brake drum 107 fixed to the shaft 106 are attached are rotated by the spring. 112 and brake shoe 108
A structure in which the brake drum 109 is pressed in a direction in which the brake drum 107 is pressed against the brake drum 107 is generally adopted.

Problems to be Solved by the Invention In the conventional device described above, the stop timing of intermittent drive is
Since it depends on the braking force of the brake, it is difficult to obtain highly accurate timing, and when driving at high speed, the ratchet wheel 1
050 overrun is likely to occur (・), and there are other disadvantages such as wear of the brake shoes and feed pawls due to long-term use, which requires time and effort for maintenance, and furthermore, as shown in Fig. 11. Moreover, the stop 9 operation becomes unsmooth, causing a significant impact on the intermittent drive device and the driven device, and the device is likely to be damaged.

In addition, various intermittent drive devices have been proposed for the purpose of eliminating these drawbacks, but most of them have the above-mentioned drawbacks to a greater or lesser extent, and no satisfactory device has yet been obtained.

Therefore, it is an object of the present invention to provide an intermittent drive device that can control operation and stop with high accuracy, requires no effort in maintenance and management, and can realize smooth operation and stop without causing shock. It is an object.

Means for Solving the Problems In order to achieve the above-mentioned object, the present invention provides a non-circular drive gear 2 fixed to an input shaft 1 rotating at a constant speed.
The entire outer circumference 1 of the elliptical cam 16 is meshed with a non-circular driven gear 4 fixed to an intermediate shaft 3 arranged parallel to the
A thin elastic metal external gear band 19, which is slidably fitted to the band 7, meshes with a rigid internal gear 20, which has a plurality of teeth greater than the number of teeth of the band, at diametrically symmetrical positions. The intermediate shaft 3 is fixed to the elliptical cam 16 of the reducer 5, the output shaft 6 is fixed to the external gear band 19, and the rigid internal gear 20 is fixed to the intermediate shaft 3. A crank lever 25 is connected to an eccentric cam 22 that is rotatable relative to the input shaft 1 and is connected to the internal gear 20 so as to give reciprocating rotational movement to the internal gear 20. is adopted.

In the present invention, since the input shaft and the intermediate shaft are connected by meshing with the non-circular drive gear and the non-circular driven gear, the constant speed rotational motion of the input shaft is converted into a slow rotational motion in the form of a sine curve. transmitted to.

On the other hand, a reduction gear in which a thin elastic metal external gear band is meshed with a rigid internal gear having a plurality of teeth more than the band at diametrically symmetrical positions around the entire outer circumference of the elliptical cam. For each revolution of the elliptical cam, the external gear band lags behind the internal gear by the difference in the number of teeth between the two.
It has a deceleration function in which the external gear band rotates once when the elliptical cam rotates by the number of teeth of the internal gear divided by the difference in the number of teeth. Therefore, if the internal gear is rotated in the direction of rotation of the elliptical cam by 1/2 of the rotation angle corresponding to the difference in the number of teeth with the external gear band while the elliptical cam rotates 1/2, The external gear band is in a state where it does not rotate at all with respect to the elliptical cam, and then, while the elliptical cam rotates 1/2, the internal gear is rotated in the opposite direction by 1/2 of the rotation angle. When the elliptical cam is moved, the external gear band rotates by a rotation angle corresponding to the difference in the number of teeth with respect to the cam during 1/2 rotation of the elliptical cam.

In the present invention, the intermediate shaft is fixed to the elliptical cam, the output shaft is fixed to the external gear band, and the rigid internal gear of the transmission is rotatable with respect to the intermediate shaft. is fixed to the input shaft and rotated reciprocally by a crank lever that is swung by an eccentric cam, so that the required 1/2 rotation during the sine curve slow rotation movement transmitted to the intermediate shaft as described above. Only part of the rotation is transmitted to the output shaft, and the remaining 1/2 rotation part can be used to stop the output shaft.Moreover, since the activation and stopping occur during the continuous rotation of the gear, the changes draw a smooth curve. This process does not generate shocks, and since the speed is changed by meshing gears, operation and stopping are controlled with high precision, and there is almost no wear and tear, which saves time and effort on maintenance and management. be.

Embodiment Figures 1 to 9 show an example of an embodiment applied to an intermittent feed device employed in a sewing machine in a slide fastener manufacturing device. Only the main structure of the present invention is shown with the machine frame, shaft support, drive motor, etc. omitted, and a non-circular drive gear 2 is fixed to an input shaft 1 that is rotated at a constant speed by a drive motor. The gear 2 is meshed with a non-circular driven gear 4 fixed to an intermediate shaft 3 installed parallel to the input shaft 1.

Due to the transmission caused by the engagement between the non-circular drive gear 2 and the non-circular driven gear 4, the input shaft rotates at a constant speed for 10 rotations.
The intermediate shaft 3 rotates with a rotational angular velocity change in the form of a sine curve as shown in FIG.

The above-mentioned intermediate shaft 3 is operatively connected to an output shaft 6 via a reduction gear 5 having a structure to be described later.

A toothed pulley 7 is fixed to the output shaft 6.
is interlocked and connected to a toothed pulley 11 of a drive roll shaft lO of a feed device 9 via a timing belt 8, and a feed roll 12 and a pressure roll 13 feed the slide fastener 14 intermittently, and a sewing machine 15 performs a predetermined sewing operation. It is configured to do the following.

As shown in FIGS. 1, 4 and 5, the reduction gear 5 described above has a bearing 1 on the entire outer circumference 17 of the elliptical cam 16.
8, an external gear band 19 made of thin elastic metal is slidably fitted, and this external gear band 19 is a rigid internal gear having a plurality of teeth greater than the number of teeth of the external gear band 19. 20
The elliptical cam 16 is engaged with the elliptical cam 16 at a symmetrical position on the long axis, that is, on the diameter line of the internal gear 20, the elliptical cam 16 is fixed to the intermediate shaft 3, and the external gear band 19 is engaged with the The internal gear 20 is fixed to the shaft 6, and the internal gear 20 is rotatably fitted to the intermediate shaft 3 and the output shaft 6.
It is fixed at 1.

An eccentric cam 22 is fixed to the input shaft 1, and a crank lever 25 extends from an eccentric outer ring 24 rotatably fitted to the eccentric cam 22 via a bearing 23.
is rotatably secured to a lever 27 protruding from an annular bracket 26 in the outer circumferential direction by a bolt 28, and the annular bracket 26 is concentrically connected to the casing 21 by a bolt 29.
It is fixed in place.

The above-mentioned eccentric cam 22. Crank lever 25. The casing 21, that is, the internal gear 2 via the annular bracket 26
00 rotation angle is the angle ω1 shown in FIG. It is selected as a corner.

In the reducer 5 having the above-described structure, when the input shaft 1 rotates once in the direction of arrow B in FIG. 5 and the elliptical cam 16 rotates once,
The external gear band 19 is also sequentially deformed, and the internal Ia float 2
The teeth that mesh with the internal teeth of 0 are changed, but the number of teeth of the external gear band 19 is less than the number of teeth of the internal gear 20, so for example, in the case of Fig. 5, there are 6 fewer teeth. Therefore, the teeth 31 of the external gear band 19 that were meshing with the teeth 30 of the internal gear 20 will mesh with the teeth 32 of the internal gear 20 after one revolution of the input shaft 1, that is, the elliptical cam 16. , the rotation of the input shaft 101 is such that the external gear band 19 is decelerated to a rotation of six teeth of the internal gear 20 in the direction of arrow C.

For this reason, the aforementioned eccentric cam 22. The rotation angle ω1 of the casing 21, that is, the internal gear 20, by the crank lever 25, etc. is set to three teeth of the internal gear 21, and during the first half rotation of the intermediate shaft 3, the rotation angle ω1 of the casing 21, that is, the internal gear 20 is gear gear 2
When the external gear band 19 is rotated by an angle ω1 in the direction of the arrow B, the external gear band 19 is maintained in a state where it is not rotated at all with respect to the elliptical cam 16, that is, the intermediate shaft 3.

Then, during the remaining half-turn of the intermediate shaft 3, the casing 21
That is, when the internal gear 20 is reversely rotated by an angle ω1, the teeth 31 of the external gear band 19 will move further from the position that the internal gear 20 should occupy in the first half-turn, indicated by the reference numeral 33 in FIG. The external gear band 19 is rotated by an angle ω2 equal to the angle ω1 corresponding to three teeth, and occupies a position meshing with the teeth 32.
The deceleration state caused by the above-mentioned deceleration device 5t is as shown in the performance curve shown in FIG.
Reference numeral 9 indicates that the intermediate shaft 3 does not rotate during the first half-rotation and stops, and transmits deceleration during the latter half-rotation.

Since the external gear band 19 described above is fixed to the output shaft 6, the rotation is not transmitted to the output shaft 6 during the first half of the rotation of the intermediate shaft 301, and the rotation is not transmitted to the output shaft 6 during the second half of the rotation of the intermediate shaft 3. Rotation is transmitted only at .

The transmission of rotation by the external gear band 19t described above is carried out as continuous meshing rotation with the internal gear 20, so the nine rotations at which it stops are smooth changes as shown in FIG. , this smooth change is combined with the sine curve rotational angular velocity change due to the meshing of the non-circular drive gear 2 and the non-circular longitudinal gear 4 shown in FIG. , the intermittent rotation transmitted to the output shaft 6 becomes intermittent rotation whose speed changes smoothly.

In the illustrated example, the fixed position of the eccentric cam 22 is selected on the input shaft 1 so that intermittent rotation is transmitted when the intermediate shaft 3 reaches its fastest rotation, but the eccentric cam 22 is set so that any rotational state can be transmitted. The fixed position of 22 is adjustable.

Effects The present invention has the structure 9 described above, and is composed of a reduction gear made of both non-circular driving and driven gears, an internal gear, and an external gear band that meshes with the internal gear. Because of this, the timing of activation and stop can be controlled with high precision.
Even when rotating at high speed, intermittent driving is possible without causing overrun or the like.

In addition, since the rotation speed can be smoothly changed by gear transmission, the intermittent drive device and the driven device can be operated and stopped without causing impact, and there are almost no wear parts. It also has the advantage of less damage to equipment and easier maintenance and management.

[Brief explanation of the drawing]

Figure 1 is a perspective view showing only the main structure of an example of implementation;
The figure is a plan view of the gear train shown in Fig. 1, Fig. 3 is a front view showing the meshing state of the non-circular drive gear and the non-circular driven gear, and Fig. 4 is the reduction gear shown in Fig. 1. Longitudinal cross-sectional view of
Fig. 5 is a sectional view taken along the line ■-■ in Fig. 4, Fig. 6 is a front view showing the connection structure between the eccentric cam and the annular blanket shown in Fig. 1, and Fig. 7 is a non-circular drive gear and a non-circular FIG. 8 is a diagram showing the deceleration characteristics of the reducer shown in FIGS. 4 and 5, and FIG. 9 is a diagram showing the intermittent drive characteristics of the device shown in FIG. 1. A rotational angular velocity change curve diagram, FIG. 10 is a schematic cross-sectional view of an example of a conventional intermittent drive device, and FIG. 11 is an intermittent drive characteristic line diagram of the one shown in FIG. 10. 1: Input shaft, 2: Non-circular drive gear, 3: Intermediate shaft, 4: Non-circular driven gear, 5: Reducer, 6: Output shaft, 16: Elliptical cam, 17: Outer periphery, 19: External gear band , 20: Internal gear, 22: Eccentric cam, 25: Crank lever, 26:
Annular bracket.

Claims (1)

[Claims] A non-circular drive gear (2) fixed to an input shaft (1) rotating at a constant speed is connected to an intermediate shaft (3) arranged parallel to the input shaft (1).
) is meshed with the non-circular driven gear (4) fixed to ), and is slidably fitted on the entire outer periphery (17) of the elliptical cam (16). The elliptical cam (16) of the speed reducer (5) in which the band (19) meshes with a rigid internal gear (20) having a plurality of teeth greater than the number of teeth of the band at a diametrically symmetrical position. The intermediate shaft (3) is fixed to the external gear band (19), the output shaft 6 is fixed to the external gear band (19), and the rigid internal gear (20
) is rotatable with respect to the intermediate shaft (3), and the input shaft (
1) An intermittent drive device in which a crank lever (25) connected to an eccentric cam (22) fixed to the internal gear (20) is connected to give reciprocating rotational movement to the internal gear (20).